Torque converter



April 28; 1953 F. M. M. B. SALOMON IORQUE CONVERTER 5 Sheets-Sheet 1 Filed Dec. 29, 1949 April 28, 1953 F. M. M. B. SALOMON 2,636,395

TORQUE CONVERTER Filed Dec. 29, 1949 3 Sheefos-Sheet 2 April 28, 1953 F. M. M. B. SALOMON TORQUE CONVERTER s Sheets-Sheet :5

Filed Dec. 29, 1949 Patented Apr. 28, 1953 UNITED gsr rE TORQUE CONVERTER Francois Marie Michel Bernard Salomon, Paris, France Application December 29, 1949, Serial No. 135,578

In France December 24, 1948 The present invention relates to a torque converter.

This apparatus is particularly applicable as a progressive and possibly automatic transmission device.

Some practical embodiments of the invention may be used in particular as change-speed gears and clutch mechanisms in and for road and railway vehicles, but the invention may be extensively and advantageously used in many different fields such as aviation, navy, fixed machines, etc.

In some devices according to the invention a primary or input shaft I (having an axis S) drives with rotary motion at least one mechanical unit (E) comprising members subjected to the inertia forces developed by the rotation and, in addition, one member at least of the mechanical unit (E) which will be referred to hereinafter as rotor is subjected to an auxiliary rotational velocity W which, in a specific case, may be zero.

The mechanical unit (E)-including the rotordue notably to the rotation caused by the drive from the primary shaft S will engender at least one resultant vector m which is a moment of momentum and will be referred to hereinafter as kinetic moment vector m or, for short, 11?.

? Claims. (01. 74-116) nating couples which will be referred to hereinafter as alternating torques T.

These alternating torques T producereciproeating motion about at least one axis A and this reciprocating motionis transmitted-for instance through connecting-rods-to at least onerecipro- 'cating' motion rectifier mounted-on atleast one output shaft 2 The above-named rectifier may consist of a free-wheel, a ratchet-wheel or any similar device.

By varying at least one auxiliary angular velocity W of at least one rotor it will belaossible to modify the kinetic moment vector m and.

In fact, the amplitude of the reciprocating mo-- tion of the members which drive the member-or members provided for rectifying the motion is subordinated dynamically to the aforesaid ki netic momentum vector H" and to its variations both in time and space.

Thus, by modifying the vector m it is possible to modify the'amplitude; now, as the angular velocity of the output shaft 2 is proportionallo this amplitude it also depends on the vector m and, in short, it depends notably on the auxiliary angular velocity W of the corresponding rotor.

As a specific case and for a'given value of this auxiliary angular velocity W it will be possible to declut-ch the transmission.

The variations in auxiliary angular velocity W may be controlled by the operator of the apparatus or by an automatic control device or both. A

great variety of automatic working systems may way of example a preferred embodiment of the invention.-

In the-drawings: v v

Fig. l is a longitudinal section of the torque converter;

Fig. 2 is a fragmentary sectional view along the line AB of Fig. 1; r

Fig. 3 is a fragmentary view according to the line CD of Fig. l;

Fig. 4 is a diagram in connection with Fig. 2; Figs. 5, 6 and 7 are explanatory diagrams; Fig. 8 is a modified embodiment of the rotor portion of the apparatus;

Fig. 9 .is a sectional view along theline AB of Fig. 8, and i 9 Fig. 10 is a section along the line CD of Fig. 9.

'Referr'inginow to the drawing and more par- Yticularly to Fig.1, in the embodiment given by .wayof example the torque convertergis shown having ,a primary input shaft I mounted for rotation about an axis S and a secondary or output shaft, 2 mounted for rotation about an axis T in axial alignment with theaxis S, butitwill be understood. that this shaft arrangement is only given by way of, example and may be different. .The input shaft l is journaled for rotation in abearing laprovided in the casing 3 and drives a'cylindrical hub 4 having an axis XY.

The angular relationshipv between the hub 4 I and the axis S may be varied. For this purpose,

the hub carries a-pin 5 having an axis 0 and mounted for rotation with the hub about the axis 5. The axis 0 is at right angles with the axis S and 'describes a plane at right angles with the axis S at O. t

The hub 4 is provided with tapered roller bearing Ba and Sb-(Fig. 1) but any other type of bearing may be used for this purpose, for instance ball-, needle-bearings, etc. Bushings may also be used in place of bearings.

The outer rings 8a, 8b of the bearings are operatively connected, as will be made clear present- 1y, with members adapted to transmit reciprocating motio-n'to therectiiying members mounted on the output shaft 2.

The inner ring 9 of a bearing 9, I (here a ballbearing, but a plain, roller or needle-bearing may be used as well) is fitted on for integral rotation with the hub 4. The bearing 9, ID has a geometrical axis X-Z' which formsa constant angle A with the axis XY of the hub 4. Ina specific case, the angle may be zero Ol.$11b5t&n*. tially zero.

The outer ring It acts as a centering member for a solid body of revolution H.

The outer surface of :the body it is a portion of a sphere.

. This body ll is a frotor inthe sensedefined hereinabove.

Various means may be used for imparting a real velocity of rotation 'W (i. ,e. a velocity of rotation in relation toitheliub '4 and inner ring The 'shaftl3 has keyed thereon a bevel gear -15 meshing with a pinion I l; fast-with a-sha'ft I 1 positioned at right angles to the shaft '13. The shaft (1 has a splined portioncooperating with a spring roller 18 'friotionally engaged with a friction plate [8. A spring 20 providedaround the 1111b of :the friction plate 459 "urges the latter against the roller l8 (Fig. 1). The outerperiphery it of the' pl-ate 19 .forms iarpur gear mes-hin with another spur gear 22 keyed 'pnthe input :or primary shaft 1.

The roller 48 may lac-moved along the shaft l! by means not shown inithe drawings. in .order to progressively vary the ratio vof.angular velocities vofthein utshaft 1S nd shaft 13.

Thus, the real angular velocity W impressed to the rotating body I! (Fig, .1.) willfhave any desired value within wide limits and this :velocvity ,may be obtained in a gradual manner since airiotional driveis established between the rollor l2 and theibo'dyof revolution 1H against which the roller is urged by the sprmg '23 as explained .above .It will be obvious that thisp in action is permitted by the self-al gn n bearing 1%.

Now, the manner in which reciprocating'mo- 'tionisdeveloped byt'he members carried '(Fig l) .hy theinput shaft 1, and how-this'reciprocating .motion.istransmitted'to the rectifying members ,hub t (FigsQl and 2).

"Both pins 24w we ,j' l rnaled for rotation in bearings 25a formed at each end 'of'a stir uppiece Zea (Fig. 2). The stirrup-piece 23a is .pivoted through a ball-and-socket joint file on a crank-armrfia keyed on a shaft 28a disposed in 4 parallel relationship with the input shaft l (Figs. 1, -2 and 3). Also keyed on the shaft 29a is a member 39a having pivotally mounted thereon, through pins 33a, 41a, a pair of connectin -rods 32a and 42a (Figs. 1 and 3).

Each of the connecting-rods 32a, 42a engages :.a member adapted to rectify reciprocating moft-lon 'and .ispivoted, forithis purpose, on that portion of the rectifier to which the reciprocating "motion is impressed.

rte enddrivesanother shaft .2192: parallel withrthe input shaft I through means similar to those described above with reference .to the transmission from the outer ring .ila to shaft 23a, these means =-comprising .a stirrup-piece 26?) :similar .to the 'stirnup piece 25;: described above and shown Figs. 12, 3 (and .4 show that the shaft leads 2 I with-respectto the shaft 291; :about .the axisfi Of.:'8h&fii J. ,A timelag-of will therefore result between the reciprocating movements ofshait .2911 with respectto those of shaft .291).

.These movements are transmitted through means similar .to .those illustrated in Fig. 3 to reciprocating motion rectifying members .34, .35 which are the same as members 36, 3? :and mountedon the same output shaft 2.

These rectifying members .may consist of freewheels or ratchet wheels ofanyknown-type.

.Theabove-described apparatus operates as .follo ws By impressing arotary .motion on' the primary rof inputigshaft :l with anangular velocity .theliub 4 and possibly the masses integral therewith will engender a kinetic moment vector lvl which rotates with an angular velocity 12 about theaxis .S iEig. ,5) .In a specific case, this .vector ,couldi'be .direoted along the axis 53.

.At .the same time .the solid of revolution .11 liFfig. "1) is .driven in .the relative .motion with anangular velocity WQasexplained above. Thus, .a kinetic moment vector E (Fig. 5) rotating .abouttheaxisS with an angular velocity aavill also result.

fflherrotatingavectorsm and m yield'a resultant vector it which is also rotated with an angular velocity a about the axis '8. The roles played by fthe various'kinetic moment vectors in the operation df the device will appear more clearly if reference is made to Fig. .5.

llhe'tenninal point B of the kinetic moment vector resulting from OM and om describes with t--t' perpendicular to the opposite.

- Therefore, the transmission will be declutched Estates Velma circle with radius Efi, H 'being' the lower end of the perpendicular distance from R to the axis S (Fig. 6).

According to the theorem of the kinetic moments the torque (C) produced by the motion of the system is represented by a vector equipollent }with the vector OV' which is itself equal and of reverse direction in relation to the vector V which is the velocity @he point B.

' The vector OV' (Fig. 6) corresponding at any moment to this torque (C) rotates about the axis S with an angular velocity 0. and thus engenders multiphase alternating torques having the same as the rotation frequency of the input .are imparted to the primary shaft a declutching action will result. This is extremely important especially in the motor vehicle field since it makes it possible to obtain an automatic declutching action.

'On the other hand, the alternating torques (C)' are functions notably of the vector m and, therefore, of the velocity W.

It is thus possible, by modifying this velocity W'--other things being equal-to modify the vector E and consequently the resultant vector 5.

More specifically, it may be arranged that the vector E be such that the resultant R of both vectors 1? and M will be directed alongthe axis S. This case is illustrated in Fig. '7. The components of OM and 0% according to theaxis axis S are equal and even if the angular velocity a is not zero, be-

- cause in this case the radius 51?. would be zero, the point R would have no velocity at all and th torque (C) would not be engendered.

Broadly speaking, by modifying the auxiliary velocity W of the body of revolution II the value of the torque (C) will be modified and therefore the'values of the impulses acting on the transmission members 34, 35, 36, 3?.(which are motion rectifiers such as free-wheels, ratchet,

etc.) will "also be changed. As a consequence 'thereof, for given dynamic conditions the ratio of the angular velocity 18 of the output shaftz to the angular velocity 0. of the inputshaft will be modified, s being the angle indicating the position of the output shaft.

The variations of velocity of W will be obtained very easily by displacing the. roller I8 the hub 4, which is like counter-balancing or re "ducing to zero the relative velocity W; Figs. 8, 9 and 10 deal more specifically but not exclusiveh with this hypothesis.

Referring to Figs. 8 and 9 it will be seen that, for this purpose, the hub 4 is fitted with an auxiliary sleeve 52 on which are pivotally mounted, :by means of pins 5i, a pair of frictionshoes i,

6 adapted to engage the inner surface 53 of an annular portion of the body I I.

The shoes 50 are controlled from the outsld in the following manner:

The shoes 50 are provided with extensions 5! engaging the outer ends of a pair of push-rods 55 the inner ends of which are formed with cam faces shown more particularly in Fig. 10. A thrust rod 56 (see Figs. 8 and 10), adapted to slide in a bore provided in the input shaft I, has a tapered inner end engageable with the aforesaid cam faces of the rods 55 and an outer end having a head which is kept in frictional engagement against a thrust-bearing 58 mounted on the shaft I and axially movable therealong by means of a control fork 51.

It will be apparent that when the thrust-bearing 58 is shifted to the right (Fig. 8) the inner tapered end of the rod 55 (Fig. 10) will drive the push-rods 55 against the extensions 54 of the shoes 50 which are therefore kept away from the inner surface 53 of the body II. a

On the contrary, if the thrust-bearing 58 is pushed leftward the shoes may freely engage and brake the body I I either through centrifugal forces acting on the shoes or by means of sprin members (not shown).

Thus, it will be possible to lock orunlock at will the body I I with the hub 4, i. e. the surface 53 with the auxiliary sleeve 52.

Fig. 1 shows also in a dagrammatic manner a make-and-break contact device operating in the manner described hereafter.

In various applications and notably in motor vehicles it may be advantageous to avoid or limit the so-called "free-wheel running. Free-wheel running may be briefly defined as follows: Assuming that the output shaft 2 tends to rotate at a higher speed than the input shaft I, under these conditions it may be desirable that the-output shaft tends-to drive the input shaft in order to produce, for instance, the reverse drive which is currently defined as engine braking in the case of automobiles.

This result will be obtained in a very simple manner by providing a free-wheel or pawl-andratchet mechanism BI, as such devices are more broadly defined, so that the output shaft 2 may rotate slower but not faster than the input shaft I.

' 'Should the velocity 5' tend to exceed a, the connecting device BI willbecome operative and therefore the shaft I will be driven by the shaft 2.

Of course, the invention is not restricted to the devices shown and. described hereinabove. Thus the body of revolution II may be driven through any system other than the friction drive illus- .trated, notably by using an. electric-motor .or fluid-controlled and fluid-operated devices (liquidor gas-controlled and/or -operated).

On the other hand, the body .I I may beprovided with turbine blades and a jet of compressed air may be directed against the blades; by modifying the pressure and/or velocity of the jet it will be possible to vary the velocity W of the body II.

Where, a friction drive system is used the friction roller and wheel illustrated may be replaced :by devices of t e brake class.

Regarding the output shaft drive, when motion rectifiers are utilized the arrangement may comprise any type of -motion selectors such as, for instance, various types of free-wheels or discontinuous coupling clutches, etc. a Also in accordance with the invention theefanswer fects of sinertia -.yvhich yoroduce kinetic ,mo-

ments occurring in the transformation of errorfly may be supplemented by resilient effects, .notably in the form of spring -,actions of ,any desired types.

,Itvvill be understood thatthe number of intermediate shafts such as 2%,291), -may vary at will and, more especially, this number may exceed two, the same applying also-to the number of i-rectifving members mounted on each rootout shaft, since the arrangement makes it sacs- ,sible .to provide more than one output shaft.

, ,What ,I claim is:

1.,A torque converter comp-rising at one idrivingshaft. atleast onemechanicalstructure positioned to receive the-i e tiaforces developed by the-rotation of said shaft-and comprising a :hubm k ne a variable an le with the axi of thQrSha-ft, bearings mounted-on the :said hum-at {least one auxiliary-member rotating on the said a hearings at a variable rotation velocity, other bearings mounted on "the hub, the axis of the last mentioned .roearings being the same as the axis of the hnhhinged connections moon" don vother bearings, intermediate 5 us- ;mission members nivot-ally mounted on :said hinged connections and adapted to transmit re- -ciprocadng motions to said intermediate shafts, and connecting rods for transmitting the motions of said intermediate shafts to rectifying Q mountedon said hu'b, hinged connections mountedon said bearings, second shafts parallel "to the driving s'haftand disposed aroundsa'id driv- ';in g shaft, connecting rods 'pivotably mounted on said hinged connections and adapted to "transmit multi-phased reciprocating motions tosaid;

parallel shafts, at least one other 'bearin mount- --edon the pivotably movable hub, at least one auxiliary member rotatable on the said other hearing at a variable rotational velocity, at'least one driven shaft, rectifying "members ,mounted on said driven shaft, connecting rods for transmitting the motions of the parallel shafts to Said rectifying members, and means for varying the rotational velocity of the auxiliary member.

3. A torque converter comprising at least one driving shaft, at least one mechanical structure positioned to receive the inertia forces developed by the rotation of said driving shaft and comprising ahub, amechanical axle perpendicular to the geometric axis of said driving .Shaft and rota ab e with said shaft. said hub bein n votab v movable around said mechanical axle, the axis of said hub making an angle dynamically variablcwith th axis of th rivin sha t, h rings mounted on said hub, hinged connections "mounted on said bearings, second shafts parallel to the driving shaft and disposed around said driving shaft, connecting rods 'pivota'bly "mounted on said hinged connections and adapted to transmit multi-phased reciprocating motions to :8 said parallel shafts, at least one other bearing mounted on the pivotablymovable ,hu'b, ,at least one auxiliary member rotatable on the said otherbearing at a variable rotational velocity, at

least onedriven shaft, rectifying members mount- .ed onsaid driven shaft, connecting rods fortransmitting the motions of the parallel shafts'to said "rectifying members, and means for varying the rotational velocity of the auxiliary member.

4. A torque converter comprising at least'one driving'shaftat least one mechanical structure positionedto receive theinertia forces developed by'zthe rotation :of said driving shaft and roomprising a hub, a "mechanical axle perpendicular to the geometric :axis of said driving shaft and rotatable with said shaft, said hub beingpivota-bl-y movable around :said mechanical axle, bearings mounted on :saidghub, hinged connections mounted on said bearings, second :paralleltothe drivingshaft and disposed-around said driving shaft, connecting *rods .pivotably mounted onsaid hinged connections and adapted to transmit multiphased reciprocating motions :tosaid parallel shafts, at least one other ibearing mounted on'the pivotably movable hub, at least one auxiliary member rotatable on the :said other hearing :at a variable rotational velocity, at least one driven shaft, the axis of said driven shaft being in axial alignment with-the axis .of

the driving shaft, rectifyingimembers mounted on said driven shaft, connecting rodsrforp.trans emitting the motions of the parallel shafts tolsaid rectifying member-S, and means for varying :the

rotational velocity of the auxiliary member.

5. A torque converter comprising at least one driving shaft, at least one mechanical structure positioned to receive the inertiaforces developed by'the rotation of said driving shaft and-comprising a hub, a mechanical axle perpendicular to the geometric axis of said driving shaft and rotatable with said shaft, said hub being pivotably movable around said mechanical axle, bearings mounted on said jhub, hinged connections mounted on said bearings, twosecondshafts parallel to the driving shaft and :disposed around said .dr'rvingzshaft, .in such manner that .thel-ines from the axes of said two second shafts to the axis of said driving shaft form a right angle, connecting rods pivotably mounted onssairl hinged connections and adapted to transmit multiphased reciprocating motions "to said parallel shafts, at least one other bearing mounted con the' pivota'bly movable hub, at least one auxiliary member rotatable on the said other bearing at a variable rotational velocity, at least one driven shaft, rectifying members mounted on said driven shaft, connecting rods for transmitting the motions of the parallel shafts to saidrectifying members, and means-for varying the rotational velocity of the auxiliary member.

6. A torque converter comprising at least one driving shaft, at least one mechanical structure positioned to receive the inertia forces developed by the rotation of said driving shaft and comprising a hub, a mechanical axle perpendicular to the geometric; axis of said driving shaft and rotatable with said shaft, said hub being pivotably movable around said mechanical axle, bean ings mounted on said hinged connections mounted on said bearingsgecen-d shafts barallel to the driving shaft and disposed around :said driving shaft, connecting rods pivotably mounted =on said hinged connections and adapted .to transmit rnulti-Dhased reciprocating motions :to

said parallel shafts, at least one other bearing mounted on the pivotably movable hub, at least one auxiliary member rotatable on the said other bearing at a variable rotational velocity, at least one driven shaft, rectifying members mounted on said driven shaft, connecting rods for transmitting the motions of the parallel shafts to said rectifying members, and friction means for varying the rotational velocity of the auxiliary member.

7. A torque converter comprising at least one driving shaft, at least one mechanical structure positioned to receive the inertia forces developed by the rotation of said driving shaft and comprising a hub, a mechanical axle perpendicular to the geometric axis of said driving shaft and rotatable with said shaft, said hub being pivotably movable around said mechanical axle, bearings mounted on said hub, hinged connections mounted on said bearings, second shafts parallel to the driving shaft and disposed around said driving shaft, connecting rods pivotably mounted on said hinged connections and adapted to transmit multi-phased reciprocating motions to said parallel shafts, at least one other bearing mounted on the pivotably movable hub, at least one auxiliary member rotatable on the said other bearing at a variable rotational velocity, at least one driven shaft, rectifying members mounted on said driven shaft, connecting rods for transmitting the motions of the parallel shafts to said rectifying members, and means for automatically varying the rotational velocity of the auxiliary member.

FRANCOIS MARIE MICHEL 

